EP0325758B1 - Condenseur de vapeur - Google Patents

Condenseur de vapeur Download PDF

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Publication number
EP0325758B1
EP0325758B1 EP88121053A EP88121053A EP0325758B1 EP 0325758 B1 EP0325758 B1 EP 0325758B1 EP 88121053 A EP88121053 A EP 88121053A EP 88121053 A EP88121053 A EP 88121053A EP 0325758 B1 EP0325758 B1 EP 0325758B1
Authority
EP
European Patent Office
Prior art keywords
steam
nest
cooler
condenser
bundle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88121053A
Other languages
German (de)
English (en)
Other versions
EP0325758A1 (fr
Inventor
Francisco Dr. Blangetti
Peter Stucki
Marc-Aurel Voth
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Switzerland GmbH
ABB Asea Brown Boveri Ltd
Original Assignee
ABB Asea Brown Boveri Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0325758A1 publication Critical patent/EP0325758A1/fr
Application granted granted Critical
Publication of EP0325758B1 publication Critical patent/EP0325758B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/10—Auxiliary systems, arrangements, or devices for extracting, cooling, and removing non-condensable gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/184—Indirect-contact condenser
    • Y10S165/205—Space for condensable vapor surrounds space for coolant
    • Y10S165/207—Distinct outlets for separated condensate and gas
    • Y10S165/211—Distinct outlets for separated condensate and gas including concave member adjacent to vapor outlet and partially covering a group of coolant tubes

Definitions

  • the invention relates to a steam condenser in which the steam is deposited on tubes through which cooling water flows and which are combined in separate bundles spaced apart from one another, the tubes of a bundle arranged in rows enclosing a cavity in which a cooler for the non-condensable gases is arranged.
  • Such a steam condenser is known from Swiss Patent No. 423 819.
  • the condenser tubes are arranged in several, so-called sub-bundles in a condenser housing.
  • the steam flows through an exhaust pipe into the condenser housing and is distributed in the room through flow channels. These narrow in the general direction of the flow in such a way that the flow velocity of the steam in these channels remains at least approximately constant.
  • the free inflow of steam to the outside tubes of the partial bundles is ensured.
  • the steam then flows through the bundles with a small resistance due to the low pipe depth.
  • the partial bundles are arranged in the condenser next to each other in such a way that flow channels arise between them, which appear in the sectional view in the same order of magnitude as the sub-bundles themselves.
  • the tubes in the successive rows form a self-contained wall, which is preferably of the same thickness throughout.
  • This known condenser has the advantage that due to the loose arrangement of the sub-bundles, all peripheral tubes of a sub-bundle are well supplied with steam without noticeable loss.
  • the requirement for at least approximately the same "wall thickness" of the tube-shaped sub-bundle around the cavity results in a relatively large overall height of the sub-bundle.
  • This known solution is less suitable for steam condensers of small power plants up to 100 MW electrical, in chemistry or in process engineering, in which the amount of steam generated is lower.
  • the surface capacitors in the last-mentioned systems are predominantly designed in a round shape.
  • These concepts are usually carried out with one-sided steam flushing of the bundle through a V-cut arranged in the middle of the condenser.
  • the rivers are arranged vertically from the center outwards with the air coolers on both sides of the jacket.
  • the typical weak points of these concepts lie in the lack of condensation performance of the lower pipe sections as well as in consequent subcooling and high oxygen content in the condensate, as well as in poor partial load behavior.
  • the invention is therefore based on the object of creating a capacitor of the type mentioned of any size and of a preferably simple external shape, which has the advantages of the partial bundle concepts mentioned above.
  • this is achieved in that two sub-bundles are provided which are exposed to the steam over their entire periphery, the bundle shape being selected independently of the external shape of the condenser in such a way that between the bundles on the one hand and between each bundle and the condenser wall initially one convergent _ the steam accelerating _ flow channel is formed and then a _ diverting the steam deflecting _ part is formed, and that the cooler for the non-condensable gases within a bundle is in the plane in which outside the bundle the convergent steam channel in ignores the divergent part.
  • the advantage of the invention can be seen in the fact that as a result of the deliberately implemented pressure reduction in the flow-through alleys at the level of the air cooler on both sides of the respective bundle, the steam-side pressure drop across the bundle is approximately constant, so that there is a homogeneous pressure gradient in the direction of the cooler . With this measure, good steam flushing through the bundle is achieved.
  • the steam in the alleys is decelerated to zero with pressure recovery at the level of the condensate collector. This causes an increase in the saturation temperature of the steam and thus a regression of the condensate supercooling that has taken place and the oxygen concentration in the condensate.
  • cooling water first acts on the lower tubes of each bundle, the cooler for the non-condensable gases preferably being arranged inside the lower tube bundle which is acted on first. This supports the regenerative properties of the bundle configuration.
  • the tubes of the cooler in the cavity of the bundle are provided with a cover plate, which is also designed as a closed suction channel that communicates with the cooler zone via panels.
  • the multifunctional cover plate protects the cooler pipes from the condensate running down.
  • the heat exchanger shown is a round surface condenser as it is suitable for the so-called underfloor arrangement. As a rule, such capacitors have exchange areas between 500 and 2500 m2.
  • the steam flows into the elongated condenser neck 1 via an evaporation nozzle (not shown) with which the condenser hangs on the turbine.
  • the best possible homogeneous flow field is generated therein in order to carry out a clean steam purging of the bundles 2 arranged downstream over their entire length.
  • Deflection blades 3 can be provided in the condenser neck 1 for the purpose of clean distribution of the steam.
  • the condensation chamber inside the cylindrical condenser jacket contains two separate sub-bundles 2. This has the aim, among other things, that a partial shutdown on the cooling water side can also be carried out during system operation, for example for the purpose of an inspection of the disconnected bundle on the cooling water side.
  • the independent application of cooling water is expressed by the fact that, according to FIG. 1, the water chambers are divided into two compartments by a vertical partition wall 10.
  • the bundles consist of a number of tubes 5, which are fastened at their two ends in tube plates 6. Beyond the tube sheets, the water chambers 7 are arranged.
  • there is a two-flow cooling water system selected which means that the inlet and outlet water chambers are on one side of the condenser and the reversal chambers on the other side.
  • the lower bundle part is chosen to be the first flow, ie the cooling water is introduced there. Accordingly, in FIG. 1 the lower water chamber connections form the inlet pipes 8 and the upper water chamber connections the outlet pipes 9.
  • Horizontal dividing walls 11 each divide the chambers into inlet or Outlet chambers.
  • the condensate flowing off from the bundles 2 is collected in the condensate collecting vessel 12 and from there it reaches the water / steam circuit, not shown.
  • a cavity 13 is formed in the interior of each bundle 2, in which the vapor enriched with non-condensable gases - hereinafter referred to as air - collects.
  • An air cooler 14 is accommodated in this cavity 13. The steam / air mixture flows through this air cooler, with most of the steam condensing. The rest of the mixture is suctioned off at the cold end.
  • the bundles are designed in such a way that all pipes in the periphery have a good flow of steam without noticeable pressure loss.
  • the existing flow paths between the two bundles 2 on the one hand and between each bundle and their adjacent condenser wall are designed as follows:
  • the predominant first part 15 of the flow path between the beginning and end of the bundle is designed to be convergent.
  • the flowing steam experiences a spatial acceleration with a corresponding decrease in the static pressure. This is approximately homogeneous on both sides of the bundle.
  • account must be taken of the fact that the steam mass flow becomes increasingly smaller as a result of the condensation.
  • the steam according to the invention should now be decelerated to zero speed with a simultaneous pressure recovery. This is achieved in that the second part 16 of the steam lane is made divergent. It also applies here Note that the channel expansion does not have to be optically recognizable due to the increasing decrease in the mass flow. The decisive factor is that the residual steam flowing towards the condenser bottom creates a dynamic pressure there. This deflects the steam and also supplies the lower parts of the bundle. The increase in temperature caused by the dynamic pressure benefits the condensate flowing down from pipe to pipe by heating up again if it has cooled below the saturation temperature. This ensures two advantages: There are no thermodynamic losses due to condensate hypothermia and the oxygen content of the condensate is reduced to a minimum.
  • the air cooler 14 is arranged in the interior of the bundle at the level at which the bundle of pressure runs through a relative minimum in the flow through the bundle on both sides.
  • the air cooler according to FIG. 2 is thus in the middle of the bundle, specifically in the first flow directly below the parting plane of the two flows.
  • the bundle is designed in such a way that the steam suction into the cavity 13 - taking into account the effective pressure at the pipe periphery and due to the different pipe row thickness - acts homogeneously in the radial direction over all pipes adjacent in the cavity 13. This results in a homogeneous pressure gradient and thus a clear flow direction of the steam and the non-condensable gases towards the air cooler.
  • the air cooler 14 has the task of removing the non-condensable gases from the condenser. During this process, the steam losses are to be kept as low as possible. This is achieved in that the steam / air mixture is accelerated in the direction of the suction duct 17. The high speed results in good heat transfer, which leads to extensive condensation of the residual steam. In order to accelerate the mixture, the cross section in the direction of flow is increasingly smaller, as can be seen in FIG. 3. The air is sucked off through orifices 18 into the channel 17. These screens are distributed several times over the entire length of the condenser and ensure that the suction effect is homogeneous in all compartments of the condenser.
  • a part of the wall of the suction channel 17 is also designed as a cover plate 19. This sheet is placed over the pipes of the cooler and protects them from the steam and condensate flow flowing downwards. This also specifies the direction of entry of the mixture to be cooled, namely from bottom to top towards the screens 18.
  • vapor barriers 21 The free space created by the omission of the pipes is equipped by means of vapor barriers 21.
  • the primary goal of these is to prevent steam bypass.
  • These are longitudinal, baffle-like sheets that have through openings (not shown) for the suction lines 20. These baffles are designed so that they do not prevent vertical steam or condensate exchange. In the direction of the steam lane / cooler, they form a flow obstacle that should have the same pressure drop as the original pipe.
  • an influence arrangement can also be implemented.
  • the non-condensable gases are led out of the condenser in the longitudinal direction instead of across the bundle.
  • the suction line penetrates one of the tube sheets and the corresponding water chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (4)

1. Condenseur de vapeur, dans lequel la vapeur est déposée sur des tubes parcourus par de l'eau froide, groupés en faisceaux séparés, espacés les uns des autres, dans lequel les tubes d'un faisceau disposés en lignes entourent un espace creux dans lequel est placé un refroidisseur pour les gaz non condensables, caractérisé en ce qu'il est prévu deux faisceaux partiels (2) qui sont exposés à la vapeur sur tout leur pourtour, la forme des faisceaux étant, indépendamment de la forme extérieure du condenseur, choisie de telle façon qu'entre les faisceaux (2) d'une part ainsi qu'entre chaque faisceau et la paroi du condenseur, est formé d'abord un canal d'écoulement (15) convergent _ accélérant la vapeur _ et ensuite un tronçon d'accumulation (16) divergent _ déviant la vapeur, et que le refroidisseur (14) pour les gaz non condensables à l'intérieur du faisceau se trouve dans le plan dans lequel le canal de vapeur convergent devient le tronçon divergent à l'extérieur du faisceau.
2. Condenseur de vapeur suivant la revendication 1, caractérisé en ce que, dans un guidage de l'eau de refroidissement à double flux, l'eau de refroidissement atteint d'abord les tubes inférieurs de chaque faisceau (2), le refroidisseur (14) pour les gaz non condensables étant disposé de préférence à l'intérieur du faisceau de tubes inférieur, qui est atteint en premier lieu par l'eau.
3. Condenseur de vapeur suivant la revendication 1, caractérisé en ce que les tubes du refroidisseur (14) situé dans l'espace creux (13) du faisceau (2) sont pourvus d'une tôle de recouvrement (19), qui a la forme d'un canal d'aspiration (17) fermé qui communique avec la zone du refroidisseur par des écrans (18).
4. Condenseur de vapeur suivant les revendications 2 et 3, caractérisé en ce que l'on aspire hors du canal d'aspiration, par au moins une conduite d'aspiration (20) traversant le faisceau, le mélange air-vapeur qui s'écoule du refroidisseur dans le canal d'aspiration, opération pour laquelle, à la surface de séparation entre les deux flux, il manque une, respectivement deux lignes de tubes dans l'enceinte normalement fermée, qui sont remplacées par des barrières de vapeur formant chicanes.
EP88121053A 1988-01-22 1988-12-16 Condenseur de vapeur Expired - Lifetime EP0325758B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH230/88 1988-01-22
CH23088 1988-01-22

Publications (2)

Publication Number Publication Date
EP0325758A1 EP0325758A1 (fr) 1989-08-02
EP0325758B1 true EP0325758B1 (fr) 1991-03-06

Family

ID=4182257

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88121053A Expired - Lifetime EP0325758B1 (fr) 1988-01-22 1988-12-16 Condenseur de vapeur

Country Status (7)

Country Link
US (1) US4967833A (fr)
EP (1) EP0325758B1 (fr)
AU (1) AU607036B2 (fr)
CA (1) CA1309908C (fr)
DE (1) DE3861964D1 (fr)
ES (1) ES2021132B3 (fr)
YU (1) YU239088A (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4141132C2 (de) * 1991-12-13 1995-06-29 Preussenelektra Ag Dampfkondensator
ES2089268T3 (es) * 1992-03-16 1996-10-01 Asea Brown Boveri Procedimiento y dispositivo para el tratamiento de agua en un condensador superficial.
DE4311118A1 (de) * 1993-04-05 1994-10-06 Abb Management Ag Dampfkondensator
US6269867B1 (en) 1994-12-02 2001-08-07 Hitachi, Ltd Condenser and power plant
EP0715143B1 (fr) * 1994-12-02 2003-03-26 Hitachi, Ltd. Condenseur et centrale thermique
JP3735405B2 (ja) * 1995-12-15 2006-01-18 株式会社東芝 復水器
DE19642100B4 (de) * 1996-10-12 2011-09-29 Alstom Dampfkondensator
EP0967451A1 (fr) 1998-06-24 1999-12-29 Asea Brown Boveri AG Condenseur de vapeur
US9217566B2 (en) * 2007-03-27 2015-12-22 Boyle Energy Services & Technology, Inc. Method and apparatus for commissioning power plants
RU2585584C2 (ru) 2012-02-10 2016-05-27 Альстом Текнолоджи Лтд Пароводяной контур и способ его очистки
DE102018118275A1 (de) * 2018-07-27 2020-01-30 Valeo Siemens Eautomotive Germany Gmbh Rotoranordnung für eine elektrische Maschine, elektrische Maschine für ein Fahrzeug und Fahrzeug

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1764716A (en) * 1926-02-11 1930-06-17 Elliott Co Condenser
US1796708A (en) * 1929-12-07 1931-03-17 Worthington Pump & Mach Corp Condenser
US2663547A (en) * 1949-05-25 1953-12-22 Lummus Co Condenser deaerator
US2869833A (en) * 1957-04-03 1959-01-20 Worthington Corp Modular heat exchanger
CH423819A (de) * 1965-01-15 1966-11-15 Bbc Brown Boveri & Cie Kondensationsanlage für Dampfturbinen-Abdampf
CH462212A (de) * 1967-09-08 1968-09-15 Bbc Brown Boveri & Cie Verfahren und Anlage zum Kondensieren von Dampf
JPS5327705A (en) * 1976-08-27 1978-03-15 Hitachi Ltd Multitube type heat exchanger
JPS53147103A (en) * 1977-05-27 1978-12-21 Hitachi Ltd Multitubular system heat exchager
JPS5914682B2 (ja) * 1980-09-29 1984-04-05 株式会社日立製作所 給水加熱器

Also Published As

Publication number Publication date
EP0325758A1 (fr) 1989-08-02
CA1309908C (fr) 1992-11-10
YU239088A (en) 1991-08-31
ES2021132B3 (es) 1991-10-16
AU2861889A (en) 1989-07-27
DE3861964D1 (de) 1991-04-11
US4967833A (en) 1990-11-06
AU607036B2 (en) 1991-02-21

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